Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
  • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F23/00—Mixing according to the phases to be mixed, e.g. dispersing or emulsifying
  • B01F23/50—Mixing liquids with solids
  • B01F23/59—Mixing systems, i.e. flow charts or diagrams
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
  • B01F25/60—Pump mixers, i.e. mixing within a pump
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F33/00—Other mixers; Mixing plants; Combinations of mixers
  • B01F33/80—Mixing plants; Combinations of mixers
  • B01F33/81—Combinations of similar mixers, e.g. with rotary stirring devices in two or more receptacles
  • B01F33/811—Combinations of similar mixers, e.g. with rotary stirring devices in two or more receptacles in two or more consecutive, i.e. successive, mixing receptacles or being consecutively arranged
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/008—Spacing or clearance between cylinder and piston
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/02—Packing the free space between cylinders and pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/08—Cooling; Heating; Preventing freezing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
  • F04B53/162—Adaptations of cylinders
  • F04B53/164—Stoffing boxes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/44—Free-space packings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F35/00—Accessories for mixers; Auxiliary operations or auxiliary devices; Parts or details of general application
  • B01F35/30—Driving arrangements; Transmissions; Couplings; Brakes
  • B01F2035/35—Use of other general mechanical engineering elements in mixing devices
  • B01F2035/351—Sealings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F2215/00—Auxiliary or complementary information in relation with mixing
  • B01F2215/04—Technical information in relation with mixing
  • B01F2215/0413—Numerical information
  • B01F2215/0418—Geometrical information
  • B01F2215/0422—Numerical values of angles
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F2215/00—Auxiliary or complementary information in relation with mixing
  • B01F2215/04—Technical information in relation with mixing
  • B01F2215/0413—Numerical information
  • B01F2215/0418—Geometrical information
  • B01F2215/0431—Numerical size values, e.g. diameter of a hole or conduit, area, volume, length, width, or ratios thereof
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
  • B01F2215/00—Auxiliary or complementary information in relation with mixing
  • B01F2215/04—Technical information in relation with mixing
  • B01F2215/0413—Numerical information
  • B01F2215/0436—Operational information
  • B01F2215/0468—Numerical pressure values

Definitions

• the invention relates to a high-pressure homogenizer for flowable substances loaded with particles according to the preamble of claim 1.
• the particles in a suspension are distributed as evenly as possible, i.e. homogeneously.
• the fluid to be homogenized is pumped through a homogenizer unit under pressure in a homogenizer.
• turbulence in connection with targeted shear forces and cavitation are generated in order to separate agglomerated particles within the fluid to be homogenized.
• plunger pumps are often used to pump the fluid into the homogenizing unit.
• Plunger pumps are positive displacement pumps in which the piston rod, the so-called plunger, itself represents the piston.
• the piston does not reach the cylinder wall. There is therefore no need for a seal between the lateral surface of the piston and the cylinder wall.
• the plunger can be passed through a cooling chamber. Since the plunger is mainly heated in the area that is located in the working area during operation, the cooling chamber should be adjacent to the working area of the pump. This ensures that the plunger is cooled close to the heat generation zone. It is advisable to use the fluid to be homogenized as the coolant.
• the fluid is pumped through the cooling chamber before it reaches the working space of the plunger pump. It flows around the plunger, which cools it. Starting from the cooling chamber, the fluid is finally passed on into the working space.
• the solution to the problem with a high-pressure homogenizer for with solid particles (which are here ⁇ occasionally referred to as "particles" for short) is loaded flowable substances with at least one high-pressure chamber and at least one, fluidically downstream, homogenizing unit Fluid, which usually has a viscosity of 20 mPas and more and which has previously been brought to a pressure of more than 500 bar in the at least one high-pressure chamber, to relax with complete or essentially complete swirling of the fluid.
• the high-pressure homogenizer also has a plunger pump assigned to the homogenization unit, the at least one plunger of which pressurizes the high-pressure chamber.
• the high-pressure homogenizer has a low-pressure chamber surrounding the plunger shaft for cooling the plunger.
• the low pressure chamber has an operating pressure of PN ⁇ 25 bar.
• the low-pressure chamber and the high-pressure chamber are separated from one another by a seal penetrated by the plunger.
• a high-pressure homogenizer is characterized in that the seal penetrated by the plunger is a throttle gap that is not between the plunger shaft and one of the plunger shafts (or in the absence of a noticeable disadvantage not significantly) touching, preferably rigid socket is formed.
• S / L radial annular gap height
• S / L 0.0015 applies.
• the term “length L” denotes the so-called cylindrical length. It is the length over which the annular gap - apart from the unavoidable shape tolerances - is cylindrical, so that the entry and exit areas of the gap that form a bevel or a radius are not included.
• the advantage of the plunger pump used here to feed the homogenizing unit is that it generates pulsations in the fluid flow pumped to the homogenizing unit, which help to further improve the homogenizing effect.
• the plunger pump can comprise either only one driven plunger or also several driven plungers - preferably with offset dead centers. In certain cases, the latter has the advantage that the frequency of the pulsations increases and their strength-critical amplitude is reduced.
• Homogenizing unit can be fed.
• the Plungers are only driven so that they reach their bottom dead center offset in time to the other plungers.
• the plunger shaft of the at least one plunger protrudes through the low-pressure chamber of the plunger pump, the fluid to be homogenized flows around it. The inevitable heating of the plunger during the pumping process is reduced, which increases the performance of the pump.
• the seal between the high-pressure and low-pressure chambers works in any case essentially, preferably even completely, without contact.
• the seal is well lubricated due to the inevitable leakage flow.
• the leak occurs at least as a drag leak, but generally as a gap leakage driven by differential pressure.
• the leakage flow is harmless because the leakage flow coming from the high pressure chamber is collected in the low pressure chamber and finally fed back to the high pressure chamber.
• the invention overcomes the prejudice that a gap seal with a very small gap height is out of the question for sealing a particle-laden liquid, since problems due to an accumulation of the solid particles carried into the gap with the fluid can be expected after a short time with the pressure difference in question are.
• the term “disperser” can also be used.
• pluri denotes a piston that is formed by the piston rod.
• high pressure chamber refers to the working space of the plunger pump.
• cooling chamber refers to the low-pressure chamber of the plunger pump.
• contactless seal refers to the contact of the socket of the high pressure seal with the outer surface of the plunger. Contact of the high pressure seal with other components of the plunger pump is not excluded.
• downstream fluid downstream fluid
• Homogenizing unit describes that the fluid to be homogenized flows from the high-pressure chamber to the homogenizing unit.
• the cylindrical length L of the throttle gap which is to be calculated without taking into account the bevels or curves on the face side, is at least 2/3 of the diameter of the plunger. Ideally, the cylindrical length corresponds to at least the entire diameter of the plunger.
• Such a gap length ensures that the flow velocity of the leakage flow is throttled. This not only ensures that a too large amount of leakage does not flow into the low-pressure chamber, but also prevents problems such as foaming when the leakage enters the low-pressure chamber.
• the height of the annular gap of the throttle gap is a maximum of 0.03 mm.
• the bushing taking into account its tolerance
• the plunger taking into account its tolerance
• the bushing should have a clear inner diameter of 20 mm + 0.009 mm
• the plunger should have one should have a maximum outer diameter of 20 mm - 0.02 mm, but this is currently not mandatory.
• the end face of the bushing merges into the inner circumferential surface of the bushing via a bevel.
• the bevel is preferably designed as a flat bevel with a bevel angle of around or exactly 30 ° or less, measured with respect to the longitudinal axis of the plunger. Such a flat bevel prevents or reduces this hard impact of the piston against the socket wall in cases in which the plunger moves out of its central position during operation.
• Attaching an angled bevel has proven to be particularly beneficial.
• a bevel On its side facing the high pressure chamber, such a bevel consists of a first steeper section which encloses an angle of approximately 45 ° to the longitudinal axis of the socket. This first section is followed on the side facing the sealing gap by a second bevel section with a flatter bevel angle, with a bevel angle of preferably around or exactly 30 ° or less.
• a bevel designed in this way keeps the solid particles away from the sealing gap as well as possible.
• the end face of the bushing (also) merges into the inner circumferential surface of the bushing via a bevel on its side facing the plunger drive.
• This bevel will usually be steeper than its counterpart on the side of the high-pressure chamber.
• a radius r can be provided at the relevant point on the socket.
• the "side facing the plunger drive” denotes the side facing the drive piston.
• the bushing and the plunger are preferably made of materials with different coefficients of thermal expansion.
• the coefficients of thermal expansion are ideally more than just insignificantly different from one another. If, for example, the plunger is made of ceramic and the bushing is made of steel, this leads to a self-regulation of the sealing gap. In the case of unfavorable friction conditions, which are caused, for example, by excessive particle entry into the gap, frictional heat is generated in the gap. Due to the frictional heat in connection with the different coefficients of thermal expansion of the bushing and plunger, the sealing gap tends to become larger. This leads to the gap being flushed clear again, which counteracts the potential risk of damage associated with the friction.
• the plunger consists of ceramic material.
• the plunger is preferably made of solid ceramic.
• the bushing consists of bearing metal. In this way, it is prevented that the occasional direct frictional contact between the outer surface of the plunger and the inner surface of the bushing (for example in the course of start-up processes or under the influence of fluid pulsations) leads to damage.
• the combination of the bushing and the plunger can be selected such that it can compensate for different process temperatures, essentially or at least partially. This is explained using the following example: If the process temperature rises, the fluid to be homogenized is at a higher temperature. It tends to be thinner. In a very narrow sealing gap between the bushing and the plunger, this could lead to lubrication problems and possibly even seizure. It counteracts this if the sealing gap changes its gap height due to the pairing of different materials of the bushing and the plunger in such a way that the lubrication is improved.
• the sealing gap is protected from damage due to particle accumulations in the sealing gap.
• the longitudinal axes of the bushing and of the plunger shaft moving back and forth in the bushing are aligned continuously parallel or preferably coaxially.
• each plunger by means of its own drive piston which is only assigned to it and which in turn is driven by a crankshaft.
• the drive pistons are connected to the crankshaft via pin bearings, the pin bearings being arranged at different angles around the axis of rotation of the crankshaft.
• a drive piston therefore takes on the role of a connecting rod.
• the plunger is connected to the drive piston driving it via a universal joint coupling.
• the plunger is only subjected to axial forces and remains free of forces that act radially in the direction of the bushing.
• the movement of the plunger accordingly remains straight and essentially parallel to the longitudinal axis of the bushing.
• the drive-side face of the plunger or the face of the drive piston that transmits the drive pressure forces to it is convexly curved.
• a curvature of the facing end faces of the plunger and the drive piston allows them to rest against one another without blocking the pivotability of the drive piston relative to the plunger.
• Fig. 1 Schematic representation of a high pressure homogenizer according to the invention
• Fig. 2 Isometric view of the section of the plunger pump (without high pressure chamber)
• FIG. 3 Enlarged section from FIG. 2
• Fig. 4 Top view of the plunger pump (with the high pressure chamber removed)
• FIG. 7 Partial sectional view of the first exemplary embodiment like that of FIGS. 5 and 6
• sectional view A of a third exemplary embodiment of the plunger pump 10 sectional view A of a fourth and a fifth exemplary embodiment of the plunger pump
• the basic mode of operation of the high-pressure homogenizer 1 can be seen well on the basis of the schematic illustration in FIG. 1.
• the fluid to be homogenized is initially located in the product storage container 28. From there it is first conveyed into the low-pressure chamber 7 and then into the high-pressure chamber 2 with the aid of the feed pump 29 via the lines 16.
• an overpressure is generated by the penetration of the plunger 5.
• This overpressure has the consequence that the inlet valve 30 is closed and the outlet valve 31 is opened.
• the plunger 5 is then pulled out of the high-pressure chamber 2 again, but only so far that the end face 23 of the plunger 5 is still located inside the high-pressure chamber 2.
• a negative pressure is generated in the high-pressure chamber. This negative pressure results in the closing of the outlet valve 31 and the opening of the inlet valve 30, so that liquid can flow into the high-pressure chamber 2 again.
• the high-pressure chamber 2 is sealed off from the surroundings and the low-pressure chamber 7 by the seal 8 located in the housing 18.
• the seal 8 is arranged in such a way that it surrounds the plunger 5.
• the undersize is preferably 0.015 mm to 0.03 mm, ideally around 0.02 mm. That leads to a radial gap height S from 0.075 mm to 0.015 mm. This should preferably be found on a sealing gap length L along the longitudinal axis of the plunger, which corresponds to at least 2/3 of the plunger diameter.
• the ratio S / L is 0.0015 mm.
• the plunger 5 is guided with its plunger shaft 6 through the housing 17 and the low-pressure chamber 7 located therein.
• the fluid to be homogenized accordingly flows around the plunger shaft 6 in the low-pressure chamber 7, whereby the latter is cooled.
• the sealing of the low-pressure chamber 7 from the environment takes place via the low-pressure sealing arrangement 25.
• plungers 5 are connected in series.
• the individual plungers 5 are ideally each controlled in such a way that they do not reach their bottom dead center at the same time, but rather at different times.
• Such a plunger pump 4 is shown in FIGS.
• the high pressure chamber 2 or the housing 32 forming the high pressure chamber 2 is not shown.
• the individual components of the plunger pump 4 are only provided with reference numerals on the basis of a plunger 5 and the associated elements of the plunger pump 4.
• Each plunger 5 of the plunger pump 4 is driven by a drive piston 12.
• the drive piston 12 and the plunger 5 are connected to one another via a radially flexible coupling, for example in the form of a universal joint 13, which is not explained in detail here.
• the plunger 5 protrudes through the housing cover 26, the housing 17 surrounding or forming the low-pressure chamber 7 and the housing 18 surrounding the high-pressure seal 8.
• the housing part 32 which forms the high pressure chamber 2 and is not shown in this FIG. 2 but shown in FIG. 1, adjoins the housing 18 surrounding the high pressure seal 8.
• the bores 21 are provided for fastening screws.
• two or more dowel pins 20 are attached to the housing part 18.
• the individual low-pressure chambers 7 are connected to one another via the connecting lines 19.
• the fluid to be homogenized is thus transported via an inlet 16 into one of the low-pressure chambers 7 and flows from there via the connecting lines 19 through the other low-pressure chambers 7.
• the fluid is finally passed out of the last low-pressure chamber 7 via the outlet 16. From there it flows via a line (not shown) into the high-pressure chambers 2 (also not shown).
• a radially flexible coupling is ideally used, as already briefly mentioned. More on this will be given later.
• Fig. 4 the arrangement of the plunger pump 4 is shown in the bottom view. This view shows how the cutting lines AA and DD run through the plunger pump 4.
• the sectional view of the section A-A is shown in FIG.
• the high pressure chamber 2 is indicated schematically.
• the high-pressure seal 8 for sealing the high-pressure chamber 2 consists of two flat seals 22 and a first socket 9. One of the flat seals 22 directly adjoins the high-pressure chamber 2, while the second flat seal 22 rests against the housing 17.
• the flat seals are only secondary seals for the sockets 9 and 24. Between the two flat seals 22, the socket 9 surrounding the plunger shaft 6 is arranged and held axially.
• the socket 9 sits firmly, rigidly directly in the surrounding housing.
• the installation is carried out in such a way that the bushing is preloaded in the radially inward direction with a pressure which is of the same order of magnitude as the pressure which later acts in the sealing gap and acts in a radially outward direction.
• a radial sealing gap which cannot be seen in FIG. 5, is formed between the bushing 9 and the lateral surface of the plunger shaft 6.
• a small amount of the fluid to be homogenized located in the high-pressure chamber 2 can escape in the direction of the low-pressure chamber 7 through the sealing gap. Due to the relationship between the height of the sealing gap and the length of the sealing gap, the pressure in the sealing gap drops continuously to the pressure of the low-pressure chamber 7, which typically leads to an overpressure in the region of 3 bar. It is usually the case that the overpressure encountered here is not above 6 bar.
• the relationship between sealing gap height and sealing gap length is like this chosen so that the amount of leakage is reduced and at the same time large enough to prevent friction problems with the particles that may be carried into the sealing gaps and carried by the liquid.
• the bushing 9 has on its end face 10 facing the drive piston 12 a bevel 40 or a bevel or a radius via which the end face merges into the inner circumferential surface. This is to prevent the edge of the end face from flaking off if there is impact-like contact with the plunger during operation.
• the plunger 5 can be provided with a bevel 41.
• the low-pressure chamber 7 is sealed off from the environment by the low-pressure sealing arrangement 25.
• FIG. 5 also illustrates the essential technical aspects of a suitable radially flexible coupling.
• the plunger 5 and the drive piston 12 are each held by a connection that is not shown in detail.
• the two connections F1 and F2 generally give the plunger 5 and the drive piston 12 a defined pivotability with respect to one another.
• the connection transmits the return stroke movement of the drive piston 12 to the plunger 5.
• One of the end faces of the plunger 5 or of the drive piston 12 is convex. This is preferably the end face of the drive piston. Typically it consists of the softer material. In this way, the drive piston 12 can "roll” on the plunger 5 by certain amounts. Any pivoting or lateral movements performed by the drive piston 12 are not transferred to the plunger 5, so that the sealing gap remains as undisturbed as possible of importance when the bushing 9 is installed radially essentially immovably in the housing part 18 surrounding it, as shown in FIG. 5.
• the section B-B shown in FIG. 6 shows how the low-pressure chambers 7 are connected to one another via the connecting lines 19.
• the first difference to the first embodiment is that the bushing 9 involved in the formation of the sealing gap is mounted in a floating manner.
• a bearing sleeve 42 made of more than only insignificantly compressible material, ideally made of a soft elastomer or rubber, is provided on its outer circumference - at least in sections, better completely.
• the radial wall thickness of the bearing sleeve 42 is typically smaller than that of the bushing 9, typically by at least a factor of 2.
• the outer casing of the bushing 9 can also be spherical instead of ideally cylindrical. This facilitates the pivoting mobility of the bushing 9 while deforming the bearing sleeve 42.
• the bearing sleeve 42 can be a discrete component in the form of a sleeve or one or more rings or a potting compound solidified in situ or a rubber body vulcanized in situ.
• a bearing collar 42 of this type allows the bushing 9 to be displaced or pivoted radially translationally by a certain amount during operation. As a result, it can adjust itself to the plunger 5 in such a way that the geometry of the sealing gap is optimized from the point of view of the sealing quality or the sealing service life.
• the elastomeric sealing rings 22 which ensure the secondary seal and which bear against the front ends of the bushing 9 also contribute to this pivotability. Different as rigid retaining rings or washers, they do not clamp the end faces between them in such a way that the bush 9 is prevented from a possible pivoting movement as a result.
• FIGS. 8a and b How the setting of the sealing gap can be imagined by pivoting the bushing 9 is shown in FIGS. 8a and b using a bushing with a cylindrical outer circumferential surface
• FIGS. 8c and d show using a bushing with a spherical outer circumferential surface how the bushing is pivoted going on.
• the socket 9 is now formed in several parts. It now consists of several, ideally three, better at least four to eight rings Ril to Ri5 built directly one behind the other and in direct contact with one another.
• the rings are permanently installed in the housing part 18 surrounding the high-pressure seal. The division into individual rings makes installation and removal during maintenance work much easier.
• a stepped gap height profile that changes more than only insignificantly between adjacent rings Ril to Ri5.
• the said first ring Ril realizes a sacrificial function: Since it has the smallest sealing gap height, it breaks particles that have penetrated into it. He himself experiences increased abrasive wear. On the other hand, however, the wear that the broken / pre-crushed particles cause the other rings Ri2 to Ri5 or Rin, which form the sealing gap with the greater sealing gap height downstream of the leakage, decreases.
• Fig. 10 shows a fourth and at the same time a fifth embodiment of the invention.
• the half of FIG. 10 shown above the central longitudinal axis represents the fourth exemplary embodiment.
• the bushing 9 is again constructed in several parts here and preferably consists of the specified number of rings Ril to Rin.
• each of the rings is now elastically supported on its outer circumferential surface, as has been described above in the context of the second exemplary embodiment - for example by encapsulating the outside with an elastomer compound or vulcanizing it into a rubber ring formed in situ or inserting it into a common, as a discrete one Component formed elastomer sleeve.
• each ring can - at least to a large extent - be moved independently of the other rings.
• a particularly good self-adjustment of the sealing gap geometry can thus be achieved.
• each ring has a bearing sleeve that is assigned to it alone.
• the bearing sleeve can, for example - if the necessary grooves are present - be designed as an O-ring, x-ring or some other standard component.
• the ring in question has clearance on both sides in addition to its bearing sleeve relative to the housing. In this way, a particularly high degree of mobility or self-adjustability of the socket 9 can be achieved.
• FIG. 11 shows a bushing 9 in a detailed view.
• the angled bevel can be clearly seen here.
• such a bevel attached on the high-pressure side consists of a first steeper section FA1 on its side facing the high-pressure chamber. This includes a chamfer angle Alpha 1 of 45 ° or approximately 45 ° to the longitudinal axis of the bush.
• This first section is followed by a second bevel section FA2 with a flatter bevel angle Alpha 2 on the side facing the sealing gap.
• the second chamfer section is preferably so narrow that no or only a reduced number of solid particles can penetrate here. This reduces the load on the annular gap with solid particles.
• Such a bevel can also be applied on the low-pressure side.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Dispersion Chemistry (AREA)
• Details Of Reciprocating Pumps (AREA)
• Reciprocating Pumps (AREA)
• Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
• Disintegrating Or Milling (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=76730247

Family Applications (1)

Country Status (7)

Family Cites Families (10)

• 2020
  • 2020-06-05 DE DE102020003401.2A patent/DE102020003401A1/de active Pending
• 2021
  • 2021-06-01 CN CN202180040610.2A patent/CN115702292A/zh active Pending
  • 2021-06-01 US US18/000,779 patent/US20230294050A1/en active Pending
  • 2021-06-01 JP JP2022574560A patent/JP2023530230A/ja active Pending
  • 2021-06-01 EP EP21736506.3A patent/EP4182560A1/de active Pending
  • 2021-06-01 WO PCT/DE2021/000104 patent/WO2021244689A1/de active Application Filing
  • 2021-06-01 KR KR1020237000155A patent/KR20230017908A/ko not_active Application Discontinuation

Also Published As

Similar Documents

Legal Events